WO2009104439A1

WO2009104439A1 - Heat exchanger arranged in ceiling-buried air conditioner, and ceiling-buried air conditioner

Info

Publication number: WO2009104439A1
Application number: PCT/JP2009/050702
Authority: WO
Inventors: 拓也松田; 石橋　晃; 青木　正則; 齊藤　信; 相武李
Original assignee: 三菱電機株式会社
Priority date: 2008-02-20
Filing date: 2009-01-20
Publication date: 2009-08-27
Also published as: EP2219002A4; EP2219002A1; AU2009216419A1; JP2009198055A; JP4610626B2; AU2009216419B2; US20100205993A1

Abstract

Disclosed is a heat exchanger (100) comprising plate fins (1) laminated at an interval, and a heat transfer pipe (2) inserted vertically into the plate fins (1) and formed to have a plurality of straight pipe portion (2s) and bent pipe portions (2r) for causing the end portions of the straight pipe portion (2s) to communicate with each other. The plate fins (1) are cut and raised to form first slit fins (3a) protruding to the side of one face and second slit fins (3b) protruding to the side of the other face. The straight pipe portions (21a) are arranged zigzag and in parallel to each other such that the 'step pitch (Dp)' or the interval between the individual axes in the step direction and the 'row pitch (Lp)' or the interval in the row direction have relations of '4 mm ≤ D ≤ 6mm, 14 mm ≤ Dp ≤ 17 mm, and 7 mm ≤ Lp ≤ 10 mm' with respect to the external diameter (D) of the heat transfer pipe (2).

Description

Heat exchanger and ceiling-embedded air conditioner installed in ceiling-embedded air conditioner

The present invention relates to a heat exchanger and a ceiling-embedded air conditioner disposed in a ceiling-embedded air conditioner, and more particularly to a fin-tube-type ceiling-embedded air conditioner for exchanging heat between a refrigerant and a fluid such as a gas. The present invention relates to a heat exchanger disposed in a machine, a ceiling-embedded air conditioner using a heat exchanger disposed in the ceiling-embedded air conditioner, and the like.

A conventional fin tube type heat exchanger is composed of a plurality of plate-like fins arranged parallel to each other at a predetermined interval, and a meandering heat transfer tube passing through the plate-like fins in the normal direction, Heat exchange is performed between the air flowing between the plate fins and the refrigerant flowing inside the heat transfer tube.
In recent years, from the viewpoint of preventing global warming, reduction of energy consumption of air conditioners and reduction of the amount of refrigerant used as a working fluid have been strongly demanded. Miniaturization is required.
On the other hand, in order to ensure comfort, the gas passing wind speed is kept low from the viewpoint of suppressing noise increase, so that the heat transfer on the air side remains lower than the heat transfer coefficient inside the heat transfer tube. Therefore, the heat transfer on the air side is improved by increasing the heat transfer area on the air side.

In other words, due to demands for downsizing heat exchangers and installation space limitations, the number of heat exchangers installed in the air flow direction (stage direction) can be increased, or the length of the heat transfer tube plate fins in the stacking direction (straight pipe) The size of the heat exchanger is not increased by extending the heat exchanger area by extending the length of the same part) or by reducing the heat transfer tube diameter, reducing the fin pitch, or A method of increasing the heat transfer area of the heat exchanger by increasing the number of installed rows in the row direction is adopted. For example, before, heat exchanger tube diameter was about 10 mm, fin pitch was about 1.5 mm, and heat exchangers with two rows were commercialized, but recently the heat transfer tube diameter is about 7 mm. The fin pitch is narrowed to about 1.1 mm, and heat exchangers with three or more rows have been commercialized.

And the heat transfer tube outer diameter D is in the range of 3 mm ≦ D ≦ 7.5 mm,
1.2D ≦ Lp ≦ 1.8D
2.6D ≦ Dp ≦ 3.5D
At this time, Lp: the row pitch in the gas passage direction of the heat transfer tube Dp: the heat transfer performance is improved by setting the step pitch in the direction perpendicular to the gas passage direction of the heat transfer tube (step direction). The invention is intended to improve the heat transfer performance and promote gas mixing in the cut-and-raised part by forming a plurality of slit fins projecting on both sides of the metal plate in a direction perpendicular to the gas passage direction and in the step direction. Is disclosed (for example, see Patent Document 1).

JP 63-3188 (page 2-3, FIG. 4)

However, Patent Document 1 does not mention the type of air conditioner in which the heat exchanger is installed. For example, in a ceiling-embedded air conditioner, the ratio of the pressure loss of the heat exchanger to the total pressure loss of the air flow is about 50%. There are few problems that cause an increase in power and noise level. Therefore, when the heat exchanger is arranged in the ceiling-embedded air conditioner, the design should place more importance on the heat transfer performance than the ventilation resistance of the heat exchanger.

Furthermore, when the diameter of the heat transfer tube is reduced, the refrigerant pressure loss increases as the refrigerant flow rate in the heat transfer tube increases, so that the amount of heat exchange as an evaporator decreases.

The present invention has been made to solve such a problem, and has a high heat transfer performance "a heat exchanger disposed in a ceiling-embedded air conditioner", and such a "heat exchanger disposed in a ceiling-embedded air conditioner" An object is to provide a “ceiling embedded air conditioner” using a “heat exchanger”.

The heat exchanger disposed in the ceiling-embedded air conditioner according to the present invention,
A plurality of plate-like fins that are stacked in parallel at a predetermined interval and through which gas passes, and a heat transfer tube that passes through the plate-like fins while meandering, and through which the working fluid passes. Have
The outer diameter (D) of the heat transfer tube, the step pitch (Dp) which is the distance between the axial centers of the heat transfer tubes concentric in the step direction which is a direction perpendicular to the gas passage direction, and the transfer in the row direction which is the gas passage direction. The relationship with the row pitch (Lp), which is the distance between the axes of the heat tubes, is
4mm ≦ D ≦ 6mm
14mm ≦ Dp ≦ 17mm
7mm ≦ Lp ≦ 10mm
It is characterized by being.

In the heat exchanger disposed in the ceiling-embedded air conditioner according to the present invention, the outer diameter (D) of the heat transfer tube is “4 mm ≦ D ≦ 6 mm”, and the step pitch (Dp) of the heat transfer tube is “14 mm ≦ Dp”. ≦ 17 mm ”and the row pitch (Lp) in the row direction of the heat transfer tubes is“ 7 mm ≦ Lp ≦ 10 mm ”, so that a“ heat exchanger arranged in a ceiling-embedded air conditioner ”having high heat transfer performance Obtainable.

The top view which shows the part explaining the heat exchanger arrange | positioned at the ceiling-embedded air conditioner which concerns on Embodiment 1 of this invention. Sectional drawing of the front view explaining the heat exchanger shown in FIG. Sectional drawing explaining the heat exchanger shown in FIG. The perspective view explaining the concept of the ceiling embedded type air conditioner which concerns on Embodiment 2 of this invention. Sectional drawing explaining the concept of the ceiling-embedded air conditioner shown in FIG. The correlation diagram which shows the influence of the heat exchanger tube diameter D which acts on the heat exchanger performance parameter | index in the heat exchanger arrange | positioned at the ceiling embedded type air conditioner shown in FIG. The correlation diagram which shows the influence of the stage pitch Dp which acts on the heat exchanger performance parameter | index in the heat exchanger arrange | positioned at the ceiling embedded type air conditioner shown in FIG. The correlation diagram which shows the influence of row pitch Lp on the heat exchanger performance parameter | index in the heat exchanger arrange | positioned at the ceiling embedded type air conditioner shown in FIG. The correlation diagram which shows the influence of the fin pitch Fp which acts on the heat exchanger performance parameter | index in the heat exchanger arrange | positioned at the ceiling embedded type air conditioner shown in FIG. The top view which shows the part explaining the heat exchanger arrange | positioned at the ceiling embedded type air conditioner concerning Embodiment 3 of this invention. Sectional drawing of the front view explaining the heat exchanger shown in FIG. The top view which shows the part explaining the heat exchanger arrange | positioned at the ceiling embedded type air conditioner which concerns on Embodiment 4 of this invention. Sectional drawing explaining the heat exchanger shown in FIG. The correlation diagram explaining the effect of the slit fin in the heat exchanger shown in FIG. The correlation diagram explaining the effect of the slit fin in the heat exchanger shown in FIG. The bottom view explaining the concept of the ceiling embedded type air conditioner which concerns on Embodiment 5 of this invention. The fragmentary sectional view explaining the concept of the ceiling embedded type air conditioner shown in FIG.

[Embodiment 1]
1 and 2 illustrate a heat exchanger disposed in a ceiling-embedded air conditioner according to Embodiment 1 of the present invention. FIG. 1 is a plan view showing the part, and FIG. 2 is a front view. 3A is a cross-sectional view taken along the line AA in FIG. 1, FIG. 3B is a cross-sectional view taken along the line BB in FIG. 1, and FIG. FIG. 3D is a cross-sectional view taken along the line CC, and FIG. 3D is a cross-sectional view taken along the line HH in FIG. In addition, in the following description, about the thing which shows a common content, description of the subscript "a, b, c ..." of a code | symbol is abbreviate | omitted.
1 and 2, heat exchangers (hereinafter referred to as “heat exchangers”) 100 arranged in a ceiling-embedded air conditioner 100 are stacked in parallel with a predetermined interval therebetween, and the intervals are set as air. The plate-like fins 1 pass through and the meandering heat transfer tubes 2 inserted perpendicularly to the plate-like fins 1, and slit fins 3 are cut and raised on the surface of the plate-like fins 1. Is formed.

(Heat transfer tube)
In FIG. 1, the heat transfer tube 2 is formed of a plurality of straight tube portions 2 s and a plurality of curved tube portions 2 r that communicate the ends of the straight tube portions 2 s. The

straight pipe portions

21a and 21b, which are a part of the straight pipe portion 2s, are arranged in a direction perpendicular to the air flow direction (hereinafter referred to as “stage direction”). (Not shown) is arranged. Similarly, straight pipe portions 22a... And

straight pipe portions

23a, 23b... That are part of the straight pipe portion 2s are arranged in the step direction. In addition, since the direction of the air flow direction is referred to as “row direction”, the heat exchanger 100 is provided with only three rows of straight pipe portions 2s.
The

straight pipe portions

21a, 21b,..., The

straight pipe portions

23a, 23b,... The “step pitch Dp” which is the interval in the direction and the “row pitch Lp” which is the interval in the row direction are “4 mm ≦ D ≦ 6 mm, 14 mm ≦ Dp ≦ 17 mm, 7 mm with respect to the outer diameter D of the heat transfer tube 2. ≦ Lp ≦ 10 mm ”, for example, D = 5 mm, Dp = 15.3 mm, Lp = 8.67 mm.

(Plate fin)
1 to 3, the plate-like fin 1 is a rectangular plate material, and a plurality of through holes through which the straight pipe portion 2s of the heat transfer tube 2 passes are formed in a staggered manner.
Further, between the straight pipe portion 21a and the straight pipe portion 21b,

first slit fins

3a, 3c, 3e projecting on one surface side, and

second slit fins

3b, 3d projecting on the other surface side, , Are formed.

The

first slit fins

3a, 3c, and 3e are obtained by cutting and raising the plate-like fin 1 on one surface side. The first

slit fin planes

32a, 32c, and 32e and the first slit fin inclined surface 31a that supports the first

slit fin planes

32a, 32c, and 32e. , 31c, 31e and first slit fin slopes 33a, 33c, 33e. Therefore, the first

slit fin grooves

34a, 34c, 34e are formed in the plate-like fin 1 by such cutting and raising.
Similarly, the

second slit fins

3b and 3d are formed by cutting and raising the plate-like fin 1 on the other surface side, and the second slit fin planes 32b and 32d and the second slit fin slopes supporting the second slit fin planes. 31b, 31d and second slit fin slopes 33b, 33d. Therefore, second

slit fin grooves

34b and 34d are formed in the plate-like fin 1 by such cutting and raising.

The first slit fin groove 34a and the second slit fin groove 34b are the second slit fin groove 34b and the first slit fin groove 34c, and the first slit fin groove 34c and the second slit fin groove 34d are The second slit fin groove 34d and the first slit fin groove 34e are continuous. Therefore, a large hole is formed in a range sandwiched between the straight pipe portion 21a and the straight pipe portion 21b of the plate-like fin 1.
Note that the protruding height (H1) of the

first slit fins

3a, 3c, 3e from one surface of the plate-like fin 1 and the protruding height of the

second slit fins

3b, 3d from the other surface of the plate-like fin 1 are as follows. The height (H2) is 1/3 of the fin pitch (Fp) which is the surface interval of the plate-like fins 1, that is, “H1 = Fp / 3, H2 = Fp / 3”.

[Embodiment 2]
FIG. 4 explains the concept of the ceiling-embedded air conditioner according to Embodiment 2 of the present invention, in which (a) is a perspective view and (b) is a cross-sectional view.
In FIG. 4, a heat exchanger 100 (see Embodiment 1) is arranged in a ceiling-embedded air conditioner (hereinafter referred to as “air conditioner”) 2000. A motor 6 for driving the fan 5 is provided on the central top surface side of the unit casing 4 of the air conditioner 2000, and the fan 5 is attached to the motor 6 with the lower side serving as a suction port.
A bell mouth 7 for introducing air into the fan 5 is disposed below the fan 5. A heat exchanger 100 is arranged in a substantially annular shape surrounding the fan, and a drain pan 9 is arranged in the lower part of the heat exchanger 100. Each side of the drain pan 9 is formed with an opening that connects the secondary side of the heat exchanger 100 and the room, and communicates with the opening 10 a of the decorative panel 10 to form the air outlet 8.
A vane 8v is attached to the blowout port 8, and the blowout direction can be adjusted. Further, a front panel 10 c and a filter 10 f are arranged at the lower part of the fan 5 so as to be fitted in the center of the decorative panel 10.

The air conditioner 200 configured as described above is generally called “four-way cassette type”, and the primary side of the fan faces downward, and sucks air from the room. The sucked air passes through the filter 10f, dust and the like are removed, and the air is blown to the heat exchanger 100. In the heat exchanger 100, heat is exchanged between the air and the refrigerant, and the air that has received heat or has been taken away is blown into the room through the air outlet 8.

(Heat transfer performance and ventilation resistance)
Next, the qualitative tendency of the shape parameters of the heat exchanger 100 will be described below with respect to the heat transfer performance and the ventilation resistance of the heat exchanger 100.

(Influence of step pitch Dp)
When the step pitch Dp is increased, the “fin efficiency” defined by the distance from the outer periphery of the heat transfer tube 2 to the end of the plate-like fin 1 and the tube diameter of the heat transfer tube 2 is reduced. "Rate" decreases. Further, when the step pitch Dp is increased, the “ventilation resistance” decreases, so that “increase in air volume” can be achieved.
On the other hand, when the step pitch Dp is reduced, the “fin efficiency” is increased and the “external heat transfer coefficient” is improved, but the “ventilation resistance” is increased.

(Influence of row pitch Lp)
When the row pitch Lp is increased, the “fin efficiency” decreases and the “external heat transfer coefficient” decreases, but the heat transfer area increases, so the heat transfer performance of the heat exchanger improves. In addition, “ventilation resistance” increases and the air volume decreases.
On the other hand, when the row pitch Lp is reduced, the “fin efficiency” is increased and the “external heat transfer coefficient” is improved, but the heat transfer area is reduced, so that the heat transfer performance of the heat exchanger is reduced. In addition, “ventilation resistance” decreases, and “increase in air volume” can be achieved.
As described above, each shape parameter of the heat exchanger has an optimum value, and in order to quantitatively evaluate this, the heat transfer characteristics and the ventilation resistance of the heat exchanger are calculated by the method described below.

The heat transfer coefficient α [W / m 2 K] between air and the plate fin is generally defined by the following equation.
α = Nu × λ / De ・・・・・・・・・・・・・ 1
Nu = C1 * (Re * Pr * De / Lp / Ln) ^ C2 Formula 2
Re = U × De / ν
Where Nu is the Nusselt number,
Re is the Reynolds number,
Pr is the Prandtl number,
λ is the thermal conductivity of air,
ν is the kinematic viscosity coefficient of air,
C1 and C2 are constants.
In the case of normal temperature and pressure, Pr = 0.72, λ = 0.0261 [W / mK], and ν = 0.000016 [m2 / s].

Here, the representative length De [m] is defined by the following equation.
De = 4 × (Lp × Dp−π × D 2/4) × Fp / {2 × (Lp × Dp−π × D 2/4) + π × D × Fp}・・・・・・ Formula 3
The wind speed U [m / s] based on the free passing volume between the plate fins 1 and the front wind speed Uf [m / s] of the heat exchanger are defined by the following equations.
U = Uf × Lp × Dp × Fp / {(Lp × Dp−π × D 2/4) × Fp}.

Further, the fin efficiency η is defined by the following equation.
η = 1 / (1 + ψ × α) ・・・・・・・・・・・・・ 5
ψ = {(4 × Lp × Dp / π) / 2−D} 2 × (4 × Lp × Dp / π) / 2 / D / 2/6 / Ft / λf・・・・・・・ Formula 6
Here, λf [w / m · k] is the thermal conductivity of the plate fin.

On the other hand, the ventilation resistance “ΔP_hex [Pa]” between the air and the plate fin is defined by the following equation.
ΔP_hex = 2 × F × Lp × Ln × ρ × U 2 / De...
F = C3 * De / Lp / Ln + C4 * ReC5 * (De / Lp / Ln) 1 + C5
(8) where F is a friction loss coefficient, and C3, C4, and C5 are constants. Further, ρ is the density of air, and is about 1.2 [kg / m 3] in the case of normal temperature and normal pressure.

(Blower operating force)
In addition, in order to quantitatively evaluate the “blower operating force” when the heat exchanger 100 (Embodiment 1) is used in the air conditioner 200 (Embodiment 2), the fan operating force is determined by the following method. Is calculated. The fan operating force Pf [W] is defined by the following equation.
Pf = ΔP_all × Q (1) in Equation 9
= (ΔP_hex + ΔP_etc) × Q (2 in Equation 9)

Hereinafter, “ΔP_hex” was calculated using the step pitch Dp and the row pitch Lp as parameters. Moreover, the heat passage rate K of the heat exchanger was calculated by the following formula.
K = 1 / (1 / αo + Ao / Ai / αi)
αo = 1 / (Ao / (Ap + η × Af) / α) Equation 12
Ao = Ap + Af Equation 13
Here, K [W / m2K] is the total heat transfer rate of the heat exchanger,
Ao [m2] is the total heat transfer area on the air side of the heat exchanger,
Ap [m2] is the heat transfer area of the air side pipe of the heat exchanger,
Af [m2] is the air side fin heat transfer area of the heat exchanger,
Ai [m2] is the refrigerant side heat transfer area of the heat exchanger,
If the dimensions depending on the shape of the heat exchanger, the step pitch Dp, the row pitch Lp, the fin pitch Fp, and the outer diameter D of the heat transfer tube are determined, the values can be calculated. Note that the heat transfer coefficient αi [W / M2K] of the fluid flowing in the pipe of the heat exchanger is constant.

In general, the energy consumption efficiency COP of an air conditioner is defined by the ratio of the heat exchange amount and the total input. By reducing the total input, the COP is improved, that is, energy saving is achieved.
Next, the total input is the sum of the compressor input and the fan operating force Pf. The compressor manpower decreases as AoK increases, and the blower operating force pf decreases as ΔP_hex decreases.
Here, a heat exchanger performance index “AoK / ΔP ^ n” is defined as a constant n. The constant n is “n = 1” when the ratio of the ventilation resistance “ΔP_hex” to the total ventilation resistance is 100%. In the heat exchanger 100 of the air conditioner 200, the ratio to the total ventilation resistance is about Since ΔP_hex is doubled, tripled, or quadrupled, the overall ventilation resistance is 1.5 times, 2.0 times, or 2.5 times, respectively. 0.59 ".
Therefore, in the heat exchanger 100 of the air conditioner 200, the heat exchanger tube diameter D and the step pitch are set as the heat exchanger performance index “AoK / ΔP ^ 0.59” when the front wind speed U = 1 [m / s]. The relationship between Dp and row pitch Lp was evaluated. In the case of another air conditioner, for example, a room air conditioner indoor unit, the ratio of ΔP_hex to the total ventilation resistance is about 80%, so “n≈0.85”.
As the air conditioner has a larger value of n, the influence of ΔP_hex on the heat exchanger performance index “AoK / ΔP ^ n” becomes larger. In the heat exchanger 100 of the air conditioner 200, other air conditioners The effect of ΔP_hex is small compared to.

6 to 9 show the influence on the heat exchanger performance index “AoK / ΔP ^ 0.59” in the heat exchanger arranged in the ceiling-embedded air conditioner according to Embodiment 1 of the present invention. 6 is a heat transfer tube diameter D, FIG. 7 is a step pitch Dp, FIG. 8 is a row pitch Lp, and FIG. 9 is a correlation diagram with a fin pitch Fp.
FIG. 6 shows the heat exchanger performance index “AoK” with the stage pitch Dp = 15.3 mm, the row pitch Lp = 8.67 mm, the front wind speed U = 1 [m / s], and the heat transfer tube diameter D as a parameter. /ΔP^0.59 ".
When the diameter of the heat transfer tube is 4 mm or less in terms of manufacturing technology, the work efficiency is significantly reduced in the step of inserting the tube expansion rod into the heat transfer tube and bringing it into close contact with the plate fin. On the other hand, when the heat transfer tube diameter is 6 mm or more, “AoK / ΔP ^ 0.59” is remarkably reduced. However, if D ≦ 6 mm, the heat transfer tube diameter D is 3 mm compared to the case of 4 mm. %, The heat exchanger with sufficiently high heat transfer performance can be supplied.
Therefore, the heat exchanger 100 with sufficiently high heat transfer performance can be supplied without reducing the production efficiency in the range of “4 mm ≦ D ≦ 6 mm”.

FIG. 7 shows the heat exchanger performance index “AoK / ΔP ^ with the stage pitch Dp as a parameter, with the heat transfer tube diameter 5 mm, the row pitch Lp = 8.67 mm, and the front wind speed U = 1 [m / s]. It is the result of calculating “0.59”.
In the vicinity of the step pitch Dp = 15 mm, the heat exchanger performance index “AoK / ΔP ^ 0.59” shows the maximum value, and “14 mm × ≦ Dp ≦ 17 mm” is a decrease of 10% or less from the maximum value. When the step pitch Dp is 14 mm or less, in the process of bending the heat transfer tube into a hairpin shape, since the bending pitch is small, there is a possibility that the heat transfer tube becomes flat and the appearance is deteriorated, or the pressure loss in the tube is increased. is there.
On the other hand, when the step pitch Dp is 17 mm or more, it is necessary to reduce the number of paths between the heat transfer tubes when the arrangement volume of the heat exchanger is considered to be constant, but when the number of paths is reduced, the pressure loss in the pipe increases. Reduce the performance of the heat exchanger. In particular, as the heat transfer tube diameter decreases, the pressure loss inside the heat transfer tube tends to increase. Accordingly, it is desirable that the step pitch Dp is “14 mm ≦ Dp ≦ 17 mm”.

FIG. 8 shows the heat exchanger performance index “AoK / ΔP ^ 0.0 with the pipe diameter 5 mm, the step pitch 15.3 mm, the front wind speed U = 1 [m / s], and the row pitch Lp as a parameter. 59 "is calculated.
Near the line pitch Lp = 8 mm, the heat exchanger performance index “AoK / ΔP ^ 0.59” shows the maximum value, and “7 mm ≦ Lp ≦ 10 mm” is 10% or less lower than the maximum value. It becomes the heat exchanger 100 with high thermal performance.
If the row pitch Lp is smaller than 7 mm, it is difficult to form fin collars (holes and collars for inserting heat transfer tubes) on the plate-like fins in terms of manufacturing technology.
On the other hand, when the row pitch Lp is 10 mm or more, the heat passage performance K decreases due to the decrease in fin efficiency, and in addition, the ventilation resistance ΔP increases, so that the heat exchanger performance index “AoK / ΔP ^ 0.59” Is significantly reduced. Therefore, the row pitch is preferably “7 mm ≦ Lp ≦ 10 mm”.

FIG. 9 shows a heat transfer tube diameter of 5 mm. Heat exchanger with a step height of 15.3 mm, row pitch LP of 8.67 mm, front wind speed U = 1 m [m / s], and the ratio “Hl / Fp” between the height Hl of the cut and raised and the fin pitch Fp as a parameter This is a result of calculating the performance index “AoK / ΔP ^ 0.59”.
The ratio of the height H1 of the cut and raised to the pitch of the fin pitch Fp “Hl / Fp = 1/3” allows air flow at equal intervals between the base of the plate-like fin and the cut and raised, and the most efficient heat transfer Since the heat exchanger performance index “AoK / ΔP ^ 0.59” shows the maximum value, the heat exchanger 100 having sufficiently high heat transfer performance can be obtained.

[Embodiment 3]
10 and 11 illustrate a heat exchanger disposed in a ceiling-embedded air conditioner according to Embodiment 3 of the present invention. FIG. 10 is a plan view showing the part, and FIG. 11 is a front view. FIG. The same parts as those in the first embodiment are denoted by the same reference numerals, a part of the description is omitted, and the same subscripts “a, b, c... The description will be omitted.

(Plate fin)
10 and 11, the plate-like fin 301 is a rectangular plate material, and a plurality of through-holes through which the straight pipe portion 2s of the heat transfer tube 2 passes are formed in a staggered manner.
Further,

first slit fins

3a, 3c, and 3e are formed between the straight pipe portion 21a and the straight pipe portion 21b so as to protrude to one surface side. That is, the plate-like fin 301 is the same as the plate-like fin 1 (Embodiment 1) in which the

second slit fins

3b and 3d are removed (not cut and raised).

Therefore, between the first slit fin 3a and the first slit fin 3c, a plate-shaped fin strip portion 35b which is a part of the plate-shaped fin 301 is provided between the first slit fin 3c and the first slit fin 3e. There are plate-like fin strips 35d, which are part of the plate-like fins 301, respectively.
The

first slit fins

3a, 3c, and 3e have the same width in the air flow direction (referred to as “Wa” for convenience), and the plate fin strips 35b and 35d have the same width in the air flow direction (for convenience). , Referred to as “Wb”).
Thus, even when the three

first slit fins

3a, 3c, 3e are cut and raised in the row direction, the effect of the present invention can be obtained as in the first embodiment.

[Embodiment 4]
12 and 13 illustrate a heat exchanger disposed in a ceiling-embedded air conditioner according to Embodiment 4 of the present invention. FIG. 12 is a plan view showing the part, and FIG. 13 is a cross-sectional view. It is. The same parts as those in the first embodiment are denoted by the same reference numerals, a part of the description is omitted, and the same subscripts “a, b, c... The description will be omitted.

(Plate fin)
12 and 13, the plate-like fin 401 is the same as the plate-like fin 301 (Embodiment 3) from which the first slit fin 3 c is removed (not cut and raised).

Therefore, two

first slit fins

3a and 3e are formed between the straight pipe portion 21a and the straight pipe portion 21b in the row direction protruding to one surface side. And between the 1st slit fin 3a and the 1st slit fin 3e, the plate-shaped fin strip part 35c which is a part of plate-shaped fin 301 exists.
The width of the

first slit fins

3a and 3e in the air flow direction is the same (referred to as “Wa” for convenience), and the width of the plate-shaped fin strip portion 35c in the air flow direction is referred to as “Wb” for convenience.
Thus, even when the two

first slit fins

3a and 3e are cut and raised in the row direction, the effect of the present invention can be obtained as in the first embodiment.

[Effect of slit fins]
14 and 15 are correlation diagrams for explaining the effect of the slit fins in the heat exchangers shown in FIGS. 12 and 13.
In FIG. 14, the horizontal axis is the ratio “wa / wb” between the width wa in the row direction of the slit fins 3 a and the like and the width wb in the row direction of the plate-like fin strips 35 b existing between the slit fins. The vertical axis represents the heat exchanger performance index “AoK / ΔP_hex ^ 0.59”, which is the result of calculation using the former as a parameter.
From FIG. 14, when the ratio “wa / wb” is 1, that is, when “Wa: Wb = 1: 1, Wa = Wb”, the heat exchanger performance index “AoK / ΔP_hex ^ 0.59” is sufficiently It becomes a big heat exchanger.

In FIG. 15, the horizontal axis is “H2 / Fp” obtained by making the height H2 of the slit fins 3a and the like dimensionless with the fin pitch Fp, and the vertical axis is the heat exchanger performance index “AoK / ΔP_hex ^ 0.59. It is a result calculated using the former as a parameter. From FIG. 15, when the slit fin height H2 is ½ of the fin pitch Fp, the heat exchanger performance index “AoK / ΔP_hex ^ 0.59” is a sufficiently large heat exchanger.

[Embodiment 5]
16 and 17 illustrate the concept of a ceiling-embedded air conditioner according to Embodiment 5 of the present invention. FIG. 16 is a bottom view, and FIG. 17 is a partial cross-sectional view.
16 and 17, a heat exchanger 500 is included in a ceiling-embedded air conditioner (hereinafter referred to as “air conditioner”) 5000. The same parts as those in FIG. 4 (Embodiment 2) and FIG. 1 (Embodiment 1) are denoted by the same reference numerals, a part of the description is omitted, and the same contents are designated by reference numerals. The description of the subscripts “a, b...” Is omitted.
In FIG. 16, the fan 5 is attached to the central top surface side of the unit housing 4 of the air conditioner 5000 with the lower side as a suction port. Two heat exchangers 500 bent in an L shape so as to surround the fan 5 are arranged in a substantially annular shape.
In this way, by arranging two L-shaped heat exchangers 500 in a substantially annular shape, the refrigerant can be transferred to the heat transfer tube 2 as compared with the case where only one L-shaped heat exchanger is disposed in a substantially annular shape. Since the length passing through the inside can be reduced and the number of passes is doubled, the pressure loss of the refrigerant in the pipe can be reduced. This is an extremely effective means when the diameter of the heat transfer tube 2 is reduced.

Therefore, when the heat exchanger 500 is used as an evaporator, it flows in 16 passes from the evaporator refrigerant inlet direction shown in FIG. 16, and the T-shaped three-way between the second row and the third row with respect to the air flow direction. The pipe distributes to 36 passes and exits to the outlet.
Generally, when a refrigerant flows through the heat transfer tube of the heat exchanger of the evaporator, the state of the refrigerant changes in the order of the two-phase region and the superheated gas. At that time, the pressure loss “ΔP_ref” of the refrigerant is larger in the superheated gas than in the two-phase region. In the present invention, the pressure loss “ΔP_ref” of the refrigerant can be greatly reduced by the effect of increasing the number of passes from 16 passes to 36 passes between the second and third rows in the vicinity of the evaporator outlet. This is a very effective means for reducing the diameter of the heat transfer tube 2.

When the heat exchanger 500 is used as a condenser, it flows in 32 passes from the condenser refrigerant inlet direction shown in FIG. 16, and is a T-shaped three-way pipe with two rows and three rows in the air flow direction. As a result, it is merged into 16 passes and discharged to the exit.

According to the present invention, since the heat transfer performance is high, it can be widely used as various internal heat exchangers and various ceiling-embedded air conditioners equipped with the same.

Explanation of symbols

1: plate fin, 2: heat transfer tube, 2r: bent tube portion, 2s: straight tube portion, 3: slit fin, 3a: first slit fin, 3b: second slit fin, 3c: first slit fin, 3d : Second slit fin, 3e: first slit fin, 4: unit housing, 5: fan, 6: motor, 7: bell mouth, 8: air outlet, 8v: vane, 9: drain pan, 10: decorative panel, 10a: Opening part, 10c: Front panel, 10f: Filter, 21a: Straight pipe part, 21b: Straight pipe part, 21c: Straight pipe part, 22a: Straight pipe part, 23a: Straight pipe part, 31a: First slit fin Slope, 31b: second slit fin slope, 32a: first slit fin plane, 32b: second slit fin plane, 33a: first slit fin slope, 33b: second slit fin slope, 34a: first Slit fin groove, 34b: second slit fin groove, 34c: first slit fin groove, 34d: second slit fin groove, 34e: first slit fin groove, 35b: plate fin strip, 35c: plate fin strip Part, 35d: plate fin strip, 100: heat exchanger, 200: air conditioner, 2000: ceiling-embedded air conditioner, 301: plate fin, 401: plate fin, 500: heat exchanger, 5000: Embedded ceiling air conditioner, ΔP: Ventilation resistance, α: Heat transfer coefficient, αi: Heat transfer coefficient, η: Fin efficiency, Ao: Total heat transfer area on the air side, AoK / ΔP_hex ^ 0.59: Heat exchanger performance index, D: outer diameter, De: representative length, Dn: number of steps, Dp: step pitch, Fp: fin pitch, H1: height, H2: height, K: heat passage rate, Lp: row Pitch, Pf: Fan operating force, Pf: Feed Machine activation force, Q: air flow rate, Rp: row pitch, U: wind velocity, Uf: face velocity, wa: width (column direction width of the slit fin), wb: width (column direction width of the plate-like fin strip portion).

Claims

A plurality of plate-like fins that are stacked in parallel at a predetermined interval and through which gas passes, and a heat transfer tube that passes through the plate-like fins while meandering, and through which the working fluid passes. Have
The outer diameter (D) of the heat transfer tube, the step pitch (Dp) which is the distance between the axial centers of the heat transfer tubes concentric in the step direction which is a direction perpendicular to the gas passage direction, and the transfer in the row direction which is the gas passage direction. The relationship with the row pitch (Lp), which is the distance between the axes of the heat tubes, is
4mm ≦ D ≦ 6mm
14mm ≦ Dp ≦ 17mm
7mm ≦ Lp ≦ 10mm
A heat exchanger disposed in a ceiling-embedded air conditioner characterized by being:
A plurality of plate-like fins stacked in parallel with a predetermined interval from each other, through which gas passes, a heat transfer tube that passes through the plate-like fins while meandering, and through which the working fluid passes;
A first slit fin that is cut and raised parallel to the direction perpendicular to the gas passage direction and protrudes to one surface side of the plate fin;
A second slit fin that is cut and raised in parallel to the first slit fin and protrudes to the other surface side of the plate fin;
A ceiling-embedded type characterized in that a first slit groove that is a trace of the first slit fin and a second slit groove that is a trace of the second slit fin are connected to each other A heat exchanger placed in an air conditioner.
The protruding height (H1) of the first slit fin from one surface of the plate-shaped fin and the protruding height (H2) of the second slit fin from the other surface of the plate-shaped fin are the plate. It is set to 1/3 of the fin pitch (Fp) which is a surface space of the fins (H1 = Fp / 3, H2 = Fp / 3). Heat exchanger.
A plurality of plate-like fins stacked in parallel with a predetermined interval from each other, through which gas passes, a heat transfer tube that passes through the plate-like fins while meandering, and through which the working fluid passes;
A plurality of slit fins that are cut and raised parallel to the direction perpendicular to the gas passage direction and project to one surface side of the plate fin,
The width (Wa) in the gas passage direction of the slit fin is equal to the gap (Wb) in the gas passage direction between the slit grooves, which is the trace of the slit fin being cut and raised. A heat exchanger placed in a harmony machine.
The protruding height (H) of the slit fin from one surface of the plate fin is ½ of the fin pitch (Fp) which is the surface interval of the plate fin (H = Fp / 2). The heat exchanger arrange | positioned at the ceiling-embedded air conditioner of Claim 4 characterized by the above-mentioned.
The heat transfer tube is formed from a plurality of straight tube portions and a plurality of bent tube portions communicating with the straight tube portions,
6. The straight pipe portion is arranged in a staggered manner so as to form three rows in the gas passage direction. 6. The straight pipe portion is arranged in a ceiling-embedded air conditioner according to claim 1. Heat exchanger.
A housing,
A fan that is disposed in the center of the casing and that discharges air sucked from the casing possible to the side, and two heat exchange units according to any one of claims 1 to 6 disposed so as to surround the fan. And having
A ceiling-embedded air conditioner, wherein a straight pipe portion of a heat transfer tube constituting the heat exchanger is bent in an L shape.
8. When the heat exchanger is used as an evaporator, a piping path is provided for allowing the refrigerant to flow out in 32 passes by using a T-shaped three-way pipe after flowing in 16 passes. A ceiling-embedded air conditioner.
In a ceiling-embedded air conditioner that uses a refrigerant as a working fluid and includes a compressor, a throttle device, a condensing heat exchanger, and an evaporating heat exchanger,
A ceiling-embedded air conditioner in which one or both of the condensation heat exchanger and the evaporative heat exchanger uses the heat exchanger according to any one of claims 1 to 6.
10. The ceiling-embedded air conditioner according to claim 9, wherein any one of R407C, R410A, R32, isobutane, carbon dioxide, and ammonia is used as the refrigerant.